Planetary rotary internal combustion engine

ABSTRACT

An apparatus for a rotary internal combustion engine. The engine has three rotating members that orbit about the center of a three-armed rotor as the rotor rotates within a housing with three lobes. The tips of the rotating members engage the lobes and a circular cutout in the rotor as the rotor rotates. A back plate includes inlet and exhaust ports that are sequentially opened and closed by the rotating members and rotor as they move within the housing. A front plate rotates with the rotor and separates the combustion chambers from a planetary gear assembly that ensures the alignment of the rotating members as they orbit the rotor shaft. Fuel is injected after the compression cycle is initiated.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application is a continuation of application Ser. No. 11/168,912,filed Jun. 28, 2005 now U.S. Pat. No. 7,044,102, which is a continuationof application Ser. No. 10/934,001, filed Sep. 3, 2004, now U.S. Pat.No. 6,932,047, issued on Aug. 23, 2005, which claims the benefit of U.S.Provisional Application No. 60/500,117, filed Sep. 4, 2003, and U.S.Provisional Application No. 60/510,204, filed Oct. 10, 2003.

STATEMENT REGARDING FEDERALLY SPONSORED RESEARCH OR DEVELOPMENT

Not Applicable

BACKGROUND OF THE INVENTION

1. Field of Invention

This invention pertains to a rotary engine with planetary rotatingmembers. More particularly, this invention pertains to an internalcombustion engine with multivaned rotating members orbiting about arotor in a chamber housing.

2. Description of the Related Art

Rotary motors in the prior art fall into two categories: those that aredriven by steam and those that are internal combustion engines. Steamdriven rotary motors typically include an expansion chamber that appliesforce to a member, causing a rotor to rotate. Examples of such steamdriven rotary motors include U.S. Pat. No. 949,605, titled “RotaryMotor,” issued on Feb. 15, 1910, to W. Taylor; U.S. Pat. No. 3,865,086,titled “Rotary Steam Engine,” issued on Feb. 11, 1975, to C. Lee; U.S.Pat. No. 5,039,290, titled “Rotary Expander,” issued on Aug. 13, 1991,to A. Nardi; and U.S. Pat. No. 6,503,072, titled “Pressure articulatedpositive displacement, single expansion rotary engine,” issued on Jan.7, 2003, to Nardi.

Through the years, attempts at developing a rotary internal combustionengine have been made. The most successful of these attempts isexemplified by the Wankel engine disclosed in U.S. Pat. No. 4,926,816,titled “Rotary Piston Engine,” issued on May 22, 1990, to Kita, et al.The conventional Wankel engine includes a rotor housing having an innerwall of trochoidal configuration, a triangular rotor disposed in a rotorcavity of the rotor housing for rotation with its apex portions insliding contact with the inner wall of the rotor housing, and aneccentric shaft supporting the rotor.

An early example of a different type of internal combustion rotaryengine is disclosed in U.S. Pat. No. 2,454,006, titled“Internal-Combustion Rotary Engine,” issued on Nov. 16, 1948, to C. E.Plummer. This patent discloses an engine with a cylindrical casing 10with two abutments 17, 18 protruding into the annular chamber 14 formedby the casing 10 and the rotor 13. The annular chamber 14 is dividedinto a power, firing and exhaust zone 15 and a compression and intakezone 16 that are diametrically opposite each other. The rotor 13 has twospider type bladed rotatable vanes 23 that rotate when engaging theabutments 17, 18. Attached to the casing 10 is a housing 28 carrying arotatable combined firing and compression cylinder 29. Diametricallyopposite the housing 28 on the casing 10 are the intake and exhaustleads 21, 22, respectively.

U.S. Pat. No. 3,865,522, titled “Rotary Internal Combustion Engine,”issued on Feb. 11, 1975, to A. Nardi. This patent discloses an enginewith a cylindrical casing 10 having a disc-shaped central inner cavity12 with eight radial recesses or notches 14 formed in the casing 10. Amain disc or rotor 16 is sized to fit into the inner cavity 12. Therotor 16 has partial circular cavities 20, 22 formed diametricallyopposite each other. The partial circular cavities 20, 22 receive leverwheels 26, 28 that rotate within the partial circular cavities 20, 22.The lever wheels 26, 28 each have three equally spaced radial arms 30that engage the notches 14 as the rotor 16 rotates within the casing 10.The fuel intake system includes ducts 34 formed through the casing 10adjacent the notches 14. Exhaust ports 38 are formed through the body ofthe rotor 16 and communicate with an exhaust manifold 40 vented to theoutside of the casing 10. U.S. Pat. No. 4,274,374, titled “Air-CooledRotary Internal Combustion Engine,” issued on Jun. 23, 1981, to C. Lee,is an improvement on the Lee patent described above. The improvementinvolved adding air-cooling to the engine.

U.S. Pat. No. 4,481,920, titled “Rotary Internal Combustion Engine,Fluid Motor and Fluid Pump Having Planetating Gear Pistons,” issued onNov. 13, 1984, to Carr, et al., discloses an intake rotor 420 surroundedby three secondary rotors 440, all nested within reactor lobe assembly640. The valve plates 330, 230, 240 and the front case cover 150 eachmount forward of reactor lobe assembly 640 with shaft 430 ofexhaust/intake rotor 420 being journalled within the central hole ofrotating valve plate 330, stationary exhaust valve plate 240 and frontcase cover 150. Reactor lobe assembly 640 has nine internal reactorlobes 460 with spark plug access holes 195 extending through the lobes460. Also mounted within the reactor lobe assembly 640 is a pressureseal 550 and spring 650 assembly which is placed between each reactorlobe 460.

German Patent Application DE 42 42 966, dated Dec. 18, 1992, discloses arotary engine. A housing 13 encloses a cylindrically shaped rotor 2,which has four niches 4 in the circumferential surface 3. The niches 4receive pistons 5 that have a star-like shape with three lips 7 spacedabout the center of rotation 6 of the pistons 5. The inner surface 8 ofthe housing 13 has a wave-shape with troughs 18 and peaks 20. Each ofthe four peaks 20 have a spark plug 14 flanked on the leading side by aexhaust valve 16 and on the trailing side by an intake valve 15.

The pistons 5 rotate clockwise as they orbit the center 1 of the rotor2, which rotates counterclockwise and carries the pistons 5. One or moreof the lips 7 of each piston 5 continuously keeps in contact with theinner surface 8 of the housing 13 as the rotor 2 rotates within thehousing 13. The German Patent Application does not disclose or teach themechanism by which the pistons 5 rotate as they orbit the center 1 ofthe rotor 2.

FIGS. 1 and 3-9 of the German application illustrate the pistons 5moving toward the exhaust valves 16, which indicates that the engineuses a decreasing volume to push the exhaust out of the exhaust valve16. Likewise, FIGS. 2 and 3-9 illustrate the pistons 5 moving away fromthe intake valves 15, which indicates that intake air is sucked into theengine by increasing the volume of the chamber, thereby drawing theintake air into the engine.

The operation of the German engine is illustrated in FIGS. 4-9 withFIGS. 4 & 5 showing the engine beginning to rotate. FIGS. 4-9 use Romannumerals to indicate the rotor 2 position as it rotates in the housing13. The pistons 5 operate in tandem, that is, opposing pistons 5, 5″ atpositions I, III draw intake air-fuel through valves 15′, 15′″ andexhaust combustion gas through valves 16, 16″. See FIG. 6. At the sametime, the other two pistons 5′, 5′″ at positions II, IV undergocombustion 25′, 25′″ on one side and compression 24′, 24′″ on the otherside. See FIG. 6. FIG. 7 shows the positions have rotated 90° with thepositions rotated counterclockwise, but the pistons 5 at those positionsperforming the same operations. That is, the piston 5, 5″ at positionsI, III are always performing intake and exhaust. See FIGS. 6-9.Likewise, the piston 5′, 5′″ at positions II, IV are always undergoingcompression and combustion.

BRIEF SUMMARY OF THE INVENTION

According to one embodiment of the present invention, a rotary internalcombustion engine with a plurality of rotating members is provided. Therotating members orbit about the center of a rotor as the rotor rotateswithin a housing with a plurality of lobes. The tips, or apex, of therotating members engage the lobes and a circular cutout in the rotor asthe rotor rotates. As the rotating members move around the housing, thefour internal combustion cycles (intake, compression, power, andexhaust) occur. As each rotating member moves around the housing, thepower and exhaust cycles occur on the side of the rotating member vanethat is trailing and the intake and compression cycles occur on the sideof the rotating member that is leading. In particular, as one side ofthe rotating member is compressing the intake gas, another side of therotating member is undergoing the power cycle.

In one embodiment, a back plate attached to one end of the housingincludes inlet and exhaust ports that are sequentially opened and closedby the rotating members and rotor as they move within the housing. Afront plate rotates with the rotor and separates the combustion chambersfrom a planetary gear assembly that ensures the alignment of therotating members as they orbit the rotor shaft.

The intake gas aids in scavenging the combustion gas out the exhaustports. In one embodiment, the intake gas does not contain fuel, which isinjected after the compression cycle is initiated. In anotherembodiment, the intake air passes through a carburetor and an air-fuelmixture passes through the inlet ports. In one embodiment, a spark pluginitiates combustion. In another embodiment, compression ignitioninitiates combustion.

BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWINGS

The above-mentioned features of the invention will become more clearlyunderstood from the following detailed description of the invention readtogether with the drawings in which:

FIG. 1 is a perspective view of one embodiment of a rotary engine;

FIG. 2 is a perspective view of one embodiment of a rotary engine withthe front cover removed;

FIG. 3 is a perspective view of one embodiment of a rotary engineshowing the planetary gear configuration;

FIG. 4 is an exploded view of one embodiment of the rotary engine;

FIG. 5 is a perspective view of the rear of one embodiment of a rotaryengine;

FIG. 6 is a perspective view of the rear of one embodiment of a rotaryengine with the back plate removed;

FIG. 7 is a perspective view of one embodiment of the back plate;

FIG. 8 is a cross-sectional view of one embodiment of the back plate;

FIG. 9 is a perspective view of one embodiment of the rotary engineshowing one embodiment of the front support plate;

FIG. 10 is a perspective view of one embodiment of the rotating membersand rotor of the rotary engine;

FIG. 11 is a front plan view of one embodiment of the rotating membersand rotor of the rotary engine;

FIG. 12 is a front plan view of one embodiment of the housing and backplate of the rotary engine;

FIG. 13 is a perspective view of one embodiment of the rotor of therotary engine;

FIG. 14 is a perspective view of one embodiment of a rotating member ofthe rotary engine;

FIGS. 15A-F are plan views of the rotor and rotating members rotatingthrough one firing cycle; and

FIG. 16 is a pictorial view of the four internal combustion cycles.

DETAILED DESCRIPTION OF THE INVENTION

An apparatus for a rotary engine is disclosed. The embodimentillustrated in the figures is a fuel injected internal combustion enginewith rotating members that orbit around and drive the rotor. The rotaryengine 10 is adaptable to run on various fuels, including, but notlimited to, gasoline and diesel. The rotary engine 10 is adaptable burnany type of fluid fuel either with a conventional spark, compressionignition, or other type of ignition system.

FIG. 1 illustrates a perspective view of one embodiment of a rotaryengine 10. A housing 102 has a front cover 104 and a back plate 106. Thefront cover 104 and the back plate 106 are secured to the housing 102 bythrough-bolts 122 and corresponding nuts 124. A rotor shaft 108 extendsfrom the front cover 104. Visible behind the back plate 106 is amanifold 116 for the intake and exhaust ports 502, 504. Also illustratedon the side of the housing 102 is one of the three spark plugs 112 andone of the three fuel injectors 114.

FIG. 2 illustrates a perspective view of one embodiment of a rotaryengine 10 with the front cover 104 removed. An idler plate 204 isattached to a front support plate 202 with fasteners 214. The assemblyof the front support plate 202 and the idler plate 204 rotates with therotor shaft 108 and supports the idler gear shafts to rotate with therotor shaft 108. A sun gear mount 212 has an opening for the rotor shaft108 and fits within an opening in the idler plate 204. The sun gearmount 212 is adapted to be fastened to the front cover 104 and isstationary relative to the housing 102. In one embodiment, the sun gearmount 212 includes a bearing supporting the rotor shaft 108.

Visible in FIG. 2 are the through-openings 222 for receiving the enginefasteners 122. Also visible are openings 232 in the housing 102 thatcorrespond to openings 132 in the front cover 104. Alignment pins (notillustrated) inserted into the openings 232 aid in the assembly of thefront cover 104 to the housing 102.

FIG. 3 illustrates a perspective view of one embodiment of a rotaryengine 10 showing the planetary gear assembly. In this view, the idlerplate 204 and sun gear mount 212 have been removed, showing the threerotating member gears 206, the three idler gears 306, and the sun gear308. In the illustrated embodiment, all the gears 206, 306, 308 have thesame number of teeth. The sun gear 308 is stationary relative to thehousing 102, and as the rotating member gears 206 orbit about the sungear 308, the rotating member gears 206 maintain the same orientation,that is, the teeth of the rotating member gears 206 do not rotaterelative to the teeth of the sun gear 308. In one embodiment, the sungear 308 is secured to the sun gear mount 212. In another embodimentwhere the number of rotating members 1006 are not the same as the numberof lobes 1112, the rotating member gears 206 rotate so as to ensure thatthe tips 1106 of the rotating members 1006 maintain contact with thelobes 1112 as the rotating members 1006 orbit the rotor shaft 108. Thoseskilled in the art will recognize that other mechanisms can be used toorbit the rotating members 1006 about the rotor 1002 without departingfrom the scope or spirit of the present invention.

A front support plate 202 rotates relative to the housing 102, but theplate 202 is stationary relative to the rotor shaft 108. The frontsupport plate 202 has openings for the rotating member shafts 316, whichcarry the rotating member gears 206. In one embodiment, the rotatingmember shafts 316 engage bearings in the front support plate 202 andidler plate 204.

The plate 202 also supports the idler shafts 326, which carry the idlergears 306. In one embodiment, the idler shafts 326 are fixed in thefront support plate 202 and idler plate 204, and the idler gears 306rotate on the idler shafts 326. In another embodiment, the idler gears306 are fixed to the idler shafts 326 and the idler shafts 326 engagebearings in the front support plate 202 and the idler plate 204.

FIG. 4 illustrates an exploded view of one embodiment of the rotaryengine 10 showing the front cover 104, the idler plate 204, theplanetary gear configuration 206, 306, 308, the housing 102, the backplate 106, and the manifold 116. In one embodiment, the bolts 122 extendthrough the housing 102, connecting the front cover 104, the housing102, and the back plate 106 by engaging the bolts 124. In otherembodiments, the housing 102 includes studs or accepts bolts securingthe front cover 104 and the back plate 106 to the housing 102.

FIG. 5 illustrates a perspective view of the rear of one embodiment of arotary engine 10 with the manifold 116 removed. In the illustratedembodiment, the rotor shaft 108 extends through the back plate 106.Surrounding the rotor shaft 108 are the exhaust ports 502 and the inletports 504. FIG. 7 illustrates the back plate 106 and the arrangement ofthe ports 502, 504.

FIG. 6 illustrates a perspective view of the rear of one embodiment of arotary engine 10 with the back plate 106 removed. The back ring mount602 has openings that receive the rotating member shafts 316. In oneembodiment, the back ring mount 602 includes bearings for the rotatingmember shafts 316. The back ring mount 602 rotates with the rotor shaft108. In the illustrated embodiment, fasteners 604 attach the back ringmount 602 to the rotor 1002.

Illustrated in FIG. 6 are the housing alignment holes 232 that, alongwith alignment pins (not illustrated), aid in aligning the back plate106 with the housing 102.

FIG. 7 illustrates a perspective view of one embodiment of the backplate 106. FIG. 8 illustrates a cross-sectional view of one embodimentof the back plate 106. The back plate 106 is stationary with respect tothe housing 102. Alignment holes 532 aid in aligning the back plate 106with the housing 102. The back plate 106 includes through-openings 724for the fasteners 122. The three exhaust ports 502 and the three inletports 504 are through-openings in the back plate 106. The back plate 106also includes an opening 708 for passage of the rotor shaft 108. In oneembodiment, the back plate 106 includes a bearing for the rotor shaft108 as it passes through the opening 708.

The back plate 106 includes a channel 702 in which the back ring mount602 rotates relative to the back plate 106. In one embodiment, thechannel 702 provides clearance between the back ring mount 602 and theback plate 106.

FIG. 9 illustrates a perspective view of one embodiment of the rotaryengine 10 showing one embodiment of the front support plate 202 withoutthe planetary gear arrangement 206, 306, 308. The front support plate202 is stationary with respect to the rotor shaft 108 and rotates withrespect to the housing 102. In the illustrated embodiment, the frontsupport plate 202 is attached to the rotor 1002 with bolts. One end ofthe rotating member shafts 316 and one end of the idler shafts 326engage the front support plate 202. The other end of the idler shafts326 engage the idler plate 204, which is secured to the front supportplate 202.

FIG. 10 illustrates a perspective view of one embodiment of the rotaryengine 10 with the front support plate 202 removed, thereby showing therotating members 1006 and rotor 1002 of the rotary engine 10. FIG. 11illustrates a front plan view of one embodiment of the rotating members1006 and rotor 1002 of the rotary engine 10. The housing 102 has aflange 1014 and a seating surface 1012. The flange 1014 is adapted tomate with the front cover 104. The through-openings 222 in the flange1014 receive the through-bolts 122, and the alignment openings 232receive alignment pins for positioning the front cover 104.

Adjacent the seating surface 1012 is the front support plate 202. Theoutside edge of front support plate 202 is adjacent the surface 1016,which is a radial surface between the flange 1014 and the seatingsurface 1012. In the illustrated embodiment, the front surface of thefront support plate 202 is even with the front surface of the flange1014.

Fixed to the rotor shaft 108 is a rotor 1002. The rotor 1002 is shown indetail in FIG. 13. The rotor 1002 is fixed to the front support plate202 by fasteners inserted in openings 1102. The back side of the rotor1002 is similarly attached to the back ring mount 602, which rotates inthe channel 702 in the back plate 106. Accordingly, the rotor 1002, therotor shaft 108, the front support plate 202, and the back ring mount602 rotate as a unit.

Fixed to the rotating member shafts 316 are the rotating members 1006.The rotating members 1006 are shown in detail in FIG. 14. The rotatingmembers 1006 revolve about the rotor shaft 108 and rotor 1002. In theillustrated embodiment, the rotating members 1006 have three vanesending at points, or tips, 1116 that contact the inside surfaces, orlobes, 1112 of the housing 102. The back ring mount 602 is visiblebehind the rotor 1002 and the rotating members 1006. The back ring mount602 fits into the channel 702 in the back plate 106.

Visible in FIG. 11 is the back plate 106 along with the exhaust ports502 and the intake ports 504. As the rotor 1002 rotates relative to theback plate 106, the arms of the rotor 1002 and the vanes, or arms, ofthe rotating members 1006 progressively expose the exhaust ports 502 andthe intake ports 504. The ports 502, 504 are discussed along with FIGS.15A-F, which illustrate the operation of the engine 10.

In one embodiment, where the three lobes 1112 of the housing 102 connectto each other, seals 1114 are positioned. These seals 1114 are discussedalong with FIG. 12.

FIG. 12 illustrates a front plan view of one embodiment of the housing102 and back plate 106 of the rotary engine 10. The three lobes 1112 ofthe housing 102 are visible. Each lobe 1112 is joined to its adjacentlobe 1112 at a peak 1214.

In the illustrated embodiment, where the three lobes 1112 of the housing102 connect to each other are the seals 1114 that engage the outsideradial surface 1304 of the rotor 1002 and prevent fluid communicationbetween adjacent lobes 1112. The seals 1114 are formed by a slit in thetrailing side of the peak 1214, as seen by the rotor 1002 as it rotateswith the rotor shaft 108. The peaks 1214 are positioned from the centerrotor shaft 108 such that the outer surface 1304 of the rotor 1002contacts the peaks 1214. The slit allows the peak 1214 between the lobes1112 to resiliently contact the radial surface 1304 of the rotor 1002.In one embodiment, the peaks 1214 have a concave surface that mates withthe outer surface 1304 of the rotor 1002. Those skilled in the art willrecognize that other types of seals can be used to provide a sealbetween the rotor 1002 and the peaks 1214 without departing from thespirit and scope of the present invention.

FIG. 13 illustrates a perspective view of one embodiment of the rotor1002 of the rotary engine 10. The rotor 1002 has a circular shape withthree circular cutouts 1302 that define three arms 1306A, 1306B, 1306C.The portion of the circular shape not cutout forms three outer surfaces1304. As the rotor 1002 rotates within the housing the three outersurfaces 1304 form a seal intermittently with the peaks 1214 of thehousing 102. In the illustrated embodiment, the outer surfaces 1304contact the peaks 1214 for a portion of the rotation of the rotor 1002.The three circular cutouts 1302 are sized to allow each rotating member1006 to rotate within its respective cutout 1302. The three arms 1306project radially from the center of the rotor 1002 and are separated by120°. Those skilled in the art will recognize that the number ofcircular cutouts 1302 and arms 1306 can vary with the number of rotatingmembers 1006 without departing from the spirit and scope of the presentinvention.

The front and back surface of the rotor 1002 have channels 1314 adjacentto the edge of the cutouts 1302 and the outer surfaces 1304. Thechannels 1314 receive a wave spring member 1316 and a sealing member1312. The wave spring member 1316 is positioned in the bottom of thechannel 1314 and the sealing member 1312 is positioned adjacent the wavespring member. The sealing member 1312 has a rectangular cross-sectionand has a top surface extending above the respective surface of therotor 1002. The top surface of the sealing member 1312, by virtue of thewave spring member 1316, has sliding contact with the front supportplate 202 or the back plate 106. In one embodiment, the wave springmember 1316 is a sheet of spring steel having a wave shape, and themember 1316 conforms to the curve of the channel 1314.

FIG. 14 illustrates a perspective view of one embodiment of a rotatingmember 1006 of the rotary engine 10. The rotating member 1006 has asymmetrical three-vaned configuration. The outer surface 1412 of therotating member 1006, which forms the tip 1106, forms a portion ofcircle with the rotating member shaft 316 at the center. The outersurface 1412 at the tip 1106 contacts the cutout 1302 in the rotor 1002as the rotating member 1006 rotates within the cutout 1302.

In the illustrated embodiment, each tip 1106 includes a seal formed by apair of side lips 1406 with a slit 1404. The lip 1406 resilientlydeforms upon contact with the lobes 1112 by virtue of the slit 1404allowing the lip 1406 to deflect toward the rotating member shaft 316.Those skilled in the art will recognize that the type of seal at thetips 1106 can vary without departing from the spirit and scope of theinvention.

Between the tips 1106 are the side surfaces 1402 of the rotating member1006. The side surfaces 1402 are arcuate surfaces and have a contour toprovide clearance from the peaks 1214 when the rotating members 1006 arein the position illustrated in FIG. 11. The shape of the contourcontributes to the combustion parameters, including compression ratio.

The front and back surface of the rotating member 1006 have channels1416 along the rotating member sides 1402. The channels 1416 receive awave spring member 1414 and a sealing member 1406. The wave springmember 1414 is positioned in the bottom of the channel 1416 and thesealing member 1406 is positioned adjacent the wave spring member 1414.The sealing member 1416 has a rectangular cross-section and has a topsurface extending above the respective surface of the rotating member1006. The top surface of the sealing member 1416, by virtue of the wavespring member 1414, has sliding contact with the front support plate 202or the back plate 106 and back ring mount 602. In one embodiment, thewave spring member 1414 is a sheet of spring steel having a wave shape,and the member 1414 conforms to the curve of the channel 1416.

FIGS. 15A-F illustrate the rotor 1002 and rotating members 1006 rotatingthrough one firing cycle. In the figures, the rotor 1002 rotatesclockwise and the rotating members 1006 do not rotate relative to thehousing 102, but the rotating members 1006 orbit around the center ofthe rotor 1002. In the illustrated embodiment, each rotating member 1006does not rotate about its centerline, but remains oriented parallel toits starting position while translating with the circular locus of theshaft 316 motion. Each rotating member 1006 defines three fluid chambers1504, 1506, 1508 corresponding to one of the three side surfaces 1402 ofeach rotating member 1006. A reference line 1502 illustrates thetop-dead-center position of the rotor 1002. Top-dead-center is definedas the position of the rotor 1002 with any rotating member 1006positioned such that a fluid chamber has its minimum volume. In FIG.15A, the rotating member 1006 fluid chamber 1504 is at its minimumvolume with the rotor 1002 in the illustrated position. For theillustrated embodiment, the rotor 1002 has three top-dead-centerpositions located 120° apart.

The rotor 1006 rotates 120° between each top-dead-center position.During that 120° rotation, one side of each of the three rotatingmembers 1006 undergoes a power cycle 1616. As the power cycle 1616progresses on the side 1402 of the rotating member 1006 that istrailing, the intake cycle 1612 and the compression cycle 1614 areprogressing on the side 1402 of the rotating member 1006 that isleading. Accordingly, the following discussion of FIGS. 15A-F applies toeach of the components that are illustrated in triplicate, such as thethree rotating members 1006, the three inlet ports 504, the threeoutlet, or exhaust, ports 502, the three spark plugs 112, and the threefuel injectors 114.

Internal combustion engines require four cycles for operation: an intakecycle 1612, a compression cycle 1614, a power cycle 1616, and an exhaustcycle 1618. Each stroke of a four stroke reciprocating piston internalcombustion engine accomplishes one of these cycles and requires fourstrokes for every power cycle 1616. For a four stroke engine, thecrankshaft rotates twice for every power cycle 1616 for a single piston.A two-stroke reciprocating piston internal combustion engine requirestwo strokes for every power cycle 1616 and the crankshaft rotates oncefor every power cycle 1616 for a single piston. The rotary engine 10does not have reciprocating pistons. Instead, the rotating members 1006of the rotary engine 10 engage a rotor 1002, which rotates with therotating members 1006 in orbit about the rotor 1002. The planetarymotion of the rotating members 1006, in combination with the rotor 1002and the lobes 1112, accomplishes the four cycles 1612, 1614, 1616, 1618with each rotating member 1006 having three power cycles 1616 for everyrotation of the rotor 1002. The following discussion begins with thepower cycle 1616 and describes the operation of the rotary engine 10.

FIG. 15A illustrates the rotor 1002 and rotating members 1006 attop-dead-center. The rotor 1002 has three top-dead-center positionsseparated by 120°. The first fluid chamber 1504 is adjacent the peak1214 between two lobes 1112. The volume between the peak 1214 and theleading tip 1116 of the rotating member 1006 is the leading fluidchamber 1504L, and the volume between the trailing tip 1116 of therotating member 1006 and the peak 1214 is the trailing fluid chamber1504T.

In the illustrated position, air has passed from the intake port 504 andhas been compressed between the rotating member 1006 and the housing 102in the leading fluid chamber 1504L and the trailing fluid chamber 1504T.In one embodiment, the fuel injector 114 injects the fuel into thecompressed air in the leading fluid chamber 1504L at top-dead-center andthe spark plug 112 then fires, igniting the fuel-air mixture in theleading fluid chamber 1504L. In another embodiment, the fuel injector114 injects the fuel and the spark plug 112 fires within a few degreesof top-dead-center.

FIG. 15B illustrates the rotor 1002 after it rotates 20 degreesclockwise. The compressed inlet gas in the trailing fluid chamber 1504Tis forced rapidly into the leading fluid chamber 1504L across thehousing peak 1214, thereby causing turbulence in the leading fluidchamber 1504L, which increases efficiency and promotes more rapid fuelcombustion rates. The combustion gas in the leading fluid chamber 1504Lexpands, causing the rotating member 1006 to force the rotor 1002 torotate clockwise. It should be noted that there is a positive torquevector generated at top-dead-center, unlike a reciprocating pistonengine or any engine designed with an eccentric crankshaft, such as theWankel engine. This promotes higher efficiency due to greatly reducedpumping in the engine prior to top-dead-center.

FIG. 15C illustrates the rotor 1002 after it rotates another 20 degreesclockwise. The gas in the trailing fluid chamber 1504T has combined withthe leading fluid chamber 1504L into a single fluid chamber 1504. Thecombustion gas continues expanding in fluid chamber 1504, applyingpressure to the side wall 1402 of the rotating member 1006 and forcingthe rotor 1002 to continue rotating clockwise.

FIG. 15D illustrates the rotor 1002 after it rotates another 20 degreesclockwise. The combustion gas continues expanding in fluid chamber 1504.

FIG. 15E illustrates the rotor 1002 after it rotates another 20 degreesclockwise, and the power cycle started with the rotor 1002 attop-dead-center begins to end. The rotor 1002 has uncovered the exhaustport 502 and a gap will appear between the trailing edge of the rotor1002 and the adjacent trailing rotating member 1006 after the rotor 1002rotates a few more degrees. This gap allows the combustion gas in fluidchamber 1504 to flow to the exhaust port 502, thereby beginning theexhaust cycle.

FIG. 15F illustrates the rotor 1002 after it rotates another 20 degreesclockwise. The exhaust cycle continues and the intake cycle is about tobegin. The inlet port 504 is about to be exposed by the rotor 1002,allowing fresh air to enter the fluid chamber 1504. The intake air willbegin to scavenge the exhaust gas across the fluid chamber 1504 to thefluid chamber 1506A of the adjacent rotating member 1006.

Referring back to FIG. 15A, with the rotor 1002 in the top-dead-centerposition, the openings connecting the fluid chamber 1508 with the fluidchamber 1506A are equal. The exhaust gas is being scavenged with theintake gas flowing counterclockwise from the inlet port 504 in fluidchamber 1508 to the exhaust port 502 in fluid chamber 1506A. With therotor 1002 in this position, the exhaust cycle 1618 and the intake cycle1612 continue.

Referring back to FIG. 15B, the exhaust port 502 has just been coveredby the rotating member 1006. With the exhaust port 502 covered, theexhaust cycle 1618 is completed. The intake cycle 1612 is also coming toan end as the rotor 1002 and the rotating member 1006 close the fluidcommunication between the inlet port 504 and the fluid chamber 1506.

Referring back to FIG. 15C, the intake cycle 1612 is complete and thecompression cycle 1614 begins for the next power cycle 1618. The fluidchamber 1506 is now a closed chamber with a decreasing volume as therotor 1002 continues clockwise. The fluid chamber 1508 is open to theexhaust port 502 and is bounded by the rotor wall 1302 and the rotatingmember side wall 1402. The gas in the fluid chamber 1508 providescooling of the rotor 1002 and the rotating member 1006.

Referring back to FIG. 15D, the compression cycle 1614 continues as thevolume of the fluid chamber 1506 continues to decrease. The fluidchamber 1508 is open to both the exhaust port 502 and the inlet port504. The gas in the fluid chamber 1508 provides cooling of the rotor1002 and the rotating member 1006.

Referring back to FIG. 15E, the compression cycle 1614 is almostcomplete. The inlet port 504 is covered by the rotating member 1006. Theexhaust port 502 is being uncovered by the rotor 1002 in the fluidchamber 1508.

Referring back to FIG. 15F, the compressed gas in the fluid chamber 1506is divided between the trailing chamber 1506T and the leading chamber1506L, which are divided by the peak 1214. In one embodiment the peak1214 does not contact the side 1402 of the rotating member 1006 suchthat the compressed gas is not prevented from flowing between thechambers 1506T, 1506L. The fluid chamber 1504 is about to connect to thefluid chamber 1506A after the rotating member tip 1106 loses contactwith the rotor wall 1302. The combustion gas in the fluid chamber 1504will then move into the fluid chamber 1506A where it will exhaustthrough the exhaust port 502. The inlet ports 504 are not yet exposed.The rotor 1002 continues rotating clockwise to the top-dead-centerposition, where the next sequence of cycles begins again.

As is apparent from the above discussion, for each complete revolutionof the rotor 1002, there are nine power cycles 1616. Each of the threerotating members 1006 have three power cycles 1616 for every revolutionof the rotor 1002. Because the rotating members 1006 are equally spacedabout the rotor 1002, the forces developed during the power cycles 1616are balanced about the rotor 1002.

In operation, the rotor 1002 rotates clockwise, and the rotor outersurfaces 1304, as they contact the peaks 1214, provide a seal betweenadjacent fluid chambers 1504, 1506, 1508. The rotating members 1006rotate, relative to the rotor 1002, counterclockwise. The tips 1106 ofthe rotating members 1006, as they contact the lobes 1112, provide aseal between adjacent fluid chambers 1504, 1506, 1508. The planetarygear assembly 206, 306, 308 ensures that the rotating members 1006 movewith the proper relationship with the rotor 1002.

FIG. 16 illustrates the four internal combustion cycles for a singlerotating member 1006 with three side surfaces 1402 as the rotatingmember 1006 orbits a full 360° around the rotor 1002. Three concentricrings represent the cycles for each of the side surfaces 1402, 1402′,1402″ of a rotating member 1006. The four cycles include the intakecycle 1612, the compression cycle 1614, the power cycle 1616, and theexhaust cycle 1618. The exhaust cycle 1618 and the intake cycle 1612 areseparated by a dead zone 1620 when the side surface 1402 of the rotatingmember 1006 faces the cutout region 1302 of the rotor 1002. FIG. 16depicts the 360° rotation of the rotor 1002, showing top-dead-center1602. 1602′, 1602″ at 0°, 120°, and 240°. Referring to FIG. 15A,top-dead-center is with the rotor 1002 oriented with the outer surfaces1304 centered in the lobes 1112. The following discussion applies to asingle side surface 1402 of a rotating member, which for illustrationpurposes forms one boundary of the fluid chamber 1504. It should beremembered that the four internal combustion cycles 1612, 1614, 1616,1618 repeat for each rotating member 1006 and that these cycles 1612,1614, 1616, 1618 repeat for every 120° rotation of the rotor 1002because each rotating member 1006 has three side surfaces 1402 separatedby 120°. Accordingly, these cycles 1612, 1614, 1616, 1618 will repeatnine times for each revolution of the rotor 1002.

The intake cycle 1612 begins approximately 140° before top-dead-center.The intake cycle 1612 begins when the rotating member 1002 uncovers theinlet ports 504, thereby allowing gas to enter the chamber. The inletports 504 are uncovered by the rotating members 1006 as the rotor 1002rotates from the position illustrated in FIG. 15F to the positionillustrated in FIG. 15A. The intake cycle 1612 completes when the inletports 504 are covered by the rotor 1002 as the rotor 1002 rotates fromthe position illustrated in FIG. 15A to the position illustrated in FIG.15B.

After completion of the intake cycle 1612, the compression cycle 1614begins. The compression cycle 1614 is completed when the rotor 1002 isat or near top-dead-center 1602. At this point, the gas is compressed ina chamber 1504 containing, in one embodiment, the fuel injector 114 andspark plug 112, and in another embodiment, just the spark plug 112, andin still another embodiment, without a spark plug 112 when the powercycle 1616 is initiated with compressive ignition.

The power cycle 1616 begins, in various embodiments, neartop-dead-center 1602 and continues until the rotor 1002 rotatesapproximately 70° from top-dead-center. At that point, the exhaust cycle1618 begins. The exhaust cycle 1618 continues until the rotor 1002rotates approximately 140° from top-dead-center. The exhaust cycle 1618is completed when the exhaust port 502 is covered by the rotating member1006 as the rotor 1002 rotates from the position illustrated in FIG. 15Fto the position illustrated in FIG. 15A. The location of the exhaustports 502 in relation to the inlet ports 504 are such that the exhaustports 502 are uncovered before the inlet ports 504 are exposed. In thismanner, the pressurized combustion gas can only flow out of the exhaustports 502. As the rotor 1002 rotates, the inlet ports 504 are exposedand the intake gas flows into the chamber. The inertia of the combustiongas exiting the exhaust ports 502 helps draw the intake gas through theinlet ports 504. The flow from the inlet ports 504 aids in scavengingthe combustion gas out the exhaust ports 502. Those skilled in the artwill recognize that the location of the exhaust and inlet ports 502, 504can vary, thereby changing the amount of rotation of the rotor 1002 foreach internal combustion cycle 1612, 1614, 1616, 1618 without departingfrom the spirit and scope of the present invention.

The above discussion applies to a single side surface 1402. FIG. 16illustrates the four internal combustion cycles 1612, 1614, 1616, 1618for each side surface 1402, 1402′, 1402″ for a single rotating member1006. The rotating member has three side surfaces 1402, 1402′, 1402″ andeach side surface 1402, 1402′, 1402″ experiences all four internalcombustion cycles 1612, 1614, 1616, 1618 in sequence. During a portionof the time that a first side surface 1402 is undergoing the intakecycle 1612, an adjacent second side surface 1402′ is undergoing theexhaust cycle 1618′. Because the two side surfaces 1402, 1402′ shareconnected fluid chambers 1508, 1504A, scavenging of the combustion gasdraws intake air into the chamber 1508 while the combustion gas isexhausted from chamber 1504A.

After first side surface 1402 begins the power cycle 1616, the adjacentsecond side surface 1402′ completes its intake cycle 1612′ and begins acompression cycle 1614′. After the first side surface 1402 begins itsexhaust cycle 1618, the adjacent third side surface 1402″ begins itsintake cycle 1612″. Each side surface 1402, 1402′, 1402″ sequentiallyundergoes an intake cycle 1612, 1612′, 1612″; a compression cycle 1614,1614′, 1614″; a power cycle 1616, 1616′, 1616″; and an exhaust cycle1618, 1618′, 1618″. Because of the relationship of the side surfaces1402, 1402′, 1402″ to each other and to the rotor 1002 and housing 102,the intake cycles 1612, 1612′, 1612″ and the exhaust cycles 1618, 1618′,1618″ overlap, thereby allowing scavenging to occur.

As can be seen in FIG. 16, each side surface 1402, 1402′, 1402″undergoes a different one of the four cycles: intake 1612, 1612′, 1612″,compression 1614, 1614′, 1614″, power 1616, 1616′, 1616″, and exhaust1618, 1618′, 1618″ at any one time. For example, one side surface 1402undergoes the power cycle 1616 and the exhaust cycle 1618 while theadjacent side surface 1402′ undergoes the intake cycle 1612′ and thecompression cycle 1614′, all within a 120° rotation of the rotor 1002.If the power cycle 1616, 1616′, 1616″ begins at top-dead-center of therotor 1002, then the power cycle 1616 and the exhaust cycle 1618 on oneside surface 1402 and the intake cycle 1612′ and the compression cycle1614′ on the adjacent side surface 1402′ occur as the rotor 1002 travelsfrom a first top-dead-center position 1602 to a second top-dead-centerposition 1602′. In another embodiment, the power cycle 1616, 1616′,1616″ begins at a point other than top-dead-center, for example, whenthe spark is advanced or retarded.

As the second side surface 1402′ moves with rotor 1002 from onetop-dead-center position 1602, through a second top-dead-center position1602′, to a third top-dead-center position 1602″, the second sidesurface 1402′ undergoes a portion of the intake cycle 1612′, thecompression cycle 1614′, the power cycle 1616′, and a portion of theexhaust cycle 1618′. That is, when the rotor 1002 has an angulardisplacement equal to twice the displacement of the adjacenttop-dead-center positions 1602, 1602′, 1602″, one side surface 1402 ofthe rotating member 1006 undergoes at least a portion of all four cycles1612, 1614, 1616, 1618.

It bears noting that in the illustrated embodiment, fuel injectors 114provide fuel to the compressed gas before combustion is initiated by thespark plugs 112. Accordingly, scavenging of the combustion gas by airflow from the inlet ports 504 does not involve any fuel. That is, airflowing into the inlet ports 504 mixes with the combustion gas and exitsthe exhaust ports 502 with the combustion gas as part of scavenging.Because the fuel has not yet been injected at the time of scavenging, nofuel (other than that due to incomplete combustion) exits through theexhaust ports 502. In another embodiment, the inlet ports 504 receive anair-fuel mixture and a fuel injector 114 is not necessary.

The rotary engine 10 includes various functions. The function ofintroducing fuel is implemented, in one embodiment, by the fuelinjectors 114. In another embodiment, the function of introducing a fuelinto the intake air is implemented by the intake air passing through acarburetor that mixes fuel with the intake air. The function of ignitingthe fuel is implemented, in one embodiment, by the spark plugs 112. Inanother embodiment, the function of igniting the fuel is implemented bycompressive ignition when the rotating member 1006 compresses theair-fuel mixture.

The function of orbiting the rotating members 1006 about the rotor 1002while maintaining at least one tip 1106 of the rotating member 1006 incontact with the surface of the lobe 1112 is implemented, in oneembodiment, by the planetary gears 206, 307, 308. Those skilled in theart will recognize that other mechanisms can be used to orbit therotating members 1006 about the rotor 1002 without departing from thescope or spirit of the present invention.

The function of sealing the tips 1406 of the rotating members 1006 isimplemented, in one embodiment, by the pair of side lips 1406 with aslit 1404, as illustrated in FIG. 14. The function of sealing the rotor1002 is implemented, in one embodiment, by the rotor 1002 havingchannels 1314 on the front and back of the rotor 1002. Each channel 1314receives a wave spring member 1316 and a sealing member 1312. Thefunction of sealing the rotating members 1006 is implemented, in oneembodiment, by each rotating member 1006 having channels 1416 on thefront and back of the rotating member 1006. Each channel 1416 receives awave spring member 1414 and a sealing member 1406. The function ofsealing the peaks 1214 is implemented, in one embodiment, by the seals1114 formed by a slit protruding into the trailing side of the peak1214.

The function of drawing intake air is implemented, in one embodiment, bythe rotor 1002 and rotating members 1006 rotating in the housing 102such that the inlet ports 504 are exposed and intake air is drawn intothe housing 102. The intake air is drawn into the chamber 1508 throughthe effects of scavenging. That is, as the combustion gas escapesthrough the exhaust ports 502, the inertia of the flowing combustion gasreduces the pressure over the inlet ports 504, thereby drawing theintake air into the chamber 1508. The intake cycle 1612 is describedabove with respect to FIG. 16.

The function of compressing the air is implemented, in one embodiment,by the rotating member 1006 compressing the intake air against the lobes1112 of the housing 102. The compression cycle 1614 is described abovewith respect to FIG. 16.

The function of introducing a fuel into the intake air is implemented,in one embodiment, by the fuel injectors 114 when the rotating member1006 has compressed the intake air. In another embodiment, the functionof introducing a fuel into the intake air is implemented by the intakeair passing through a carburetor that mixes fuel with the intake air.

The function of combusting the air and the fuel is implemented, in oneembodiment, by the spark plugs 112 igniting the air-fuel mixture. Inanother embodiment, combustion occurs when the air-fuel mixture iscompressed to the point where compressive ignition occurs. The powercycle 1616 is described above with respect to FIG. 16.

The function of exhausting the combusted air and fuel is implemented, inone embodiment, by the rotor 1002 and the rotating member 1006 rotatingin the housing 102 such that the exhaust ports 502 are exposed and thecombustion gas is exhausted from the housing 102. The exhaust cycle 1618is described above with respect to FIG. 16.

The function of obtaining rotary motion from the combustion isimplemented, in one embodiment, by the shaft 316 of the rotating member1006 engaging the front support plate 202 and to the rear ring 602,which are connected to the rotor 1002. Pressure from the combustion gasis applied to the side 1402 of the rotating member 1006 and thispressure is transferred to the rotating member shaft 316, whichtransfers the force to the front support plate 202 and to the rear ring602, which causes the rotor 1002 to rotate.

The function of sealing the rotary engine 10 is implemented, in variousembodiments, by the various seals. There is a seal 1114 between therotor 1002 and the peak 1214. There is a seal 1312, 1316, 1314 betweenthe sides of the rotor 1002 and the back plate 106 and the front supportplate 202. There is a seal 1406, 1414, 1416 between the front and backof the rotating member 1006 and the back plate 106 and the front supportplate 202. There is a seal 1404, 1406 at each tip 1106 of the rotatingmember 1006.

From the foregoing description, it will be recognized by those skilledin the art that a rotary engine 10 has been provided. The illustratedembodiment shows three rotating members 1006 interfacing with threelobes 1112 in the housing. In other embodiments, either or both thenumber of rotating members 1006 and the number of lobes 1112 varies.

While the present invention has been illustrated by description ofseveral embodiments and while the illustrative embodiments have beendescribed in considerable detail, it is not the intention of theapplicant to restrict or in any way limit the scope of the appendedclaims to such detail. Additional advantages and modifications willreadily appear to those skilled in the art. The invention in its broaderaspects is therefore not limited to the specific details, representativeapparatus and methods, and illustrative examples shown and described.Accordingly, departures may be made from such details without departingfrom the spirit or scope of applicant's general inventive concept.

1. A rotary engine providing internal combustion of a fuel, said rotaryengine comprising: a housing having a sidewall, an inside surface ofsaid sidewall having a plurality of lobes, adjacent ones of saidplurality of lobes separated by a peak, said housing including a backplate having a plurality of exhaust ports and a plurality of inletports; a rotor having a shaft and at least two arms, adjacent ones ofsaid at least two arms forming a circular cutout region, said rotorforming a seal with each said peak intermittently when said rotorrotates within said housing; at least one rotating member, each of saidat least one rotating member having a rotating member shaft, each saidat least one rotating member rotatable within a corresponding one ofsaid circular cutout region in said rotor, each said rotating memberhaving three tips equally spaced around said at least one rotatingmember; a gear assembly whereby said at least one rotating member orbitssaid rotor shaft and at least one of said three tips of each of said atleast one rotating member maintains contact with a corresponding one ofsaid plurality of lobes and maintains a fixed orientation when orbitingsaid rotor shaft; a means for introducing a fuel into said housing; anda means for igniting said fuel in said housing.
 2. The rotary engine ofclaim 1 wherein said housing further includes a front plate, said frontplate having a back surface facing said back plate, wherein said frontplate, said back plate, and said sidewall form a cavity in said housingin which said rotor rotates and carries said at least one rotatingmember.
 3. The rotary engine of claim 1 further including a back ringmount receiving each said rotating member shaft opposite said rotatingmember gear, said back ring received by a channel in said back plate. 4.The rotary engine of claim 1 further including an exhaust manifold fordirecting combustion gas from said plurality of exhaust ports.
 5. Therotary engine of claim 1 further including an intake manifold fordirecting air to said plurality of inlet ports.
 6. The rotary engine ofclaim 1 wherein each of said three tips of each said at least onerotating member includes a seal.
 7. The rotary engine of claim 1 whereineach of said three tips of each said at least one rotating memberincludes a means for sealing.
 8. The rotary engine of claim 1 whereinsaid rotor includes at least one side seal and said at least onerotating member includes a plurality of side seals.
 9. The rotary engineof claim 1 wherein said rotor includes means for sealing.
 10. The rotaryengine of claim 1 wherein said at least one rotating member includesmeans for sealing a front side and a back side of each said at least onerotating member.